Machine tool



Dec. 12, 1939. G. K. McKEE El' AL 2,183,297

' MACHINE TOOL 1 Filed Nov. 25, 1936 6 Sheets-Sheet 2 4t 4 a :r/

INVENTORS, GEORGE K M: KEE BY CHARLES E. BERN/7T 12, 1939. e. K. MQKEE ET AL 2,183,297

- MACHINE TOOL Filed Nov. 25, 1936 s Sheets-Sheet 5 INVENTORS, GEORGE K. McKEE BY CHARLES E. HEM/Tr W Q%EYS Dec. 12, 1939. G, K. McKEE Er AL. 2,183,297

MACHINE TOOL Filed Nov. 25, 1936 6 Sheets-Sheet 4 114% e y 9 82 :B5

INVENTORS GEORGE K. MCKEE I Q10. A BY 0mm 5, 5m,

.Dea 12, 1939. G. K. M K EE E15 2,183,297

MACHINE TOOL F110d NOV. 25, 1936 6 Sheets-Sheet 6 INVENTORS, GEORGEK. McKEE BY CHARLES E. BERN/77" atented Dee. E2, 1939 Avey Drilling Machine 2,183.29? momma roar.

Company, Oovington,

Ky., a corporation of Ohio Application November 25, 1936, Serial No. 112,724 18 Claims. (Ol.-77--32) This invention relates to improvements in machine tools and particularly to improvements in drilling machines.

. In the drilling of long holes in metallic objects, it is frequently necessary and desirable to periodically withdraw the tool from the hole for the purpose of clearing the chips and then continue the drilling for a distance, whereupon, the tool is again withdrawn, and continue this drilling and chip clearing periodically, until the hole is completely drilled or bored. The length of driling time for each step of the drilling is, of course, variable, depending upon the density or hardness of the material being drilled and the diaml3 eter of the hole. Various attempts have been made to accomplish this result, each with varying degrees of success, due to the fact that the means for accomplishing this step drilling process was of the true friction type which frequently failed, in that it failed to securely hold at successive adjustments and was, therefore, a more or less hit and miss proposition. Attempts have also been made to effect this operation by means of step bars and the like, in which each successive drilling operation wasldentical with no means for adjusting either the depth of the cut or the duration of drilling time, which is necessary, due, as was stated above, to the density or hardness of the material being operated upon 0' or the size of the drill or the hole being drilled.

By the present invention, all of these difliculties have been over-come, and it is therefore one of the principal objects of this invention to provide a step drilling machine, which is positive in its action, yet adjustable within wide limits to take care of these conditions, encountered in actual practice.

It is also an object of this invention to provide an accumulating step means which is positive in construction and operation for definitely operating the control mechanism at the necessary and desired parts.

A further object of this invention, is the provision of a step drilling control mechanism which 4 is automatic in operation, in eifecting the cyclic rapid and feed movements of the drill or other tool and insuring the parts returning to and operating at the points desired in each cycle.

A still-further object of this invention is the 50 provision of a complete control mechanismwhich is positive in its operation in snapping the control mechanism from the rapid movement to the feed movement and from the feed movement to the return rapid movement without danger of 55 over-riding the intended points of snap-over.

It is also the object of this invention to provide a mechanism to accomplish the above objects, which is relatively simple in construction and comparatively inexpensive to manufacture.

Other objects and advantages of the present in= vention should be readily apparent by reference to the following specification considered in conjunction with the accompanying drawings fon'ning a part thereof and it is to be understood that any modifications may be made in the exact 10' structural details there shown and described, within the scope of the appended claims, without departing from or exceeding the spirit of the invention. I

In the drawings:

Fig. 1 is a side elevation of a drilling machine embodying the-improvements of this invention.

Fig. 2 is a front elevation of the machine illustrated in Fig. l. a

Fig. 3 is an enlarged, elevational view of the 20 drilling head which contains the control mechanism for controlling the movement of the drill or tool mounted on said head.

Fig. 4 is an enlarged, sectionalview through the drive mechanism for the drill or other tool 23 as seen from line i-fl on Fig. 2.

Fig. 5 is a top plan view of the drilling head as seen from the top of Fig. 3.

Fig. 6 is a horizontal, sectional view through the drilling head as seen from line 6-6 on Fig. 3. 30-

Fig. 7' is an enlarged, vertical, sectional view through the forward end of the drilling head, particularly illustrating the drill or tool carrier and means for eiiecting it's reciprocation, as seen from line 1-7 on Fig. 2. 35

Fig.8 is a vertical, transverse, sectional view through the drilling head, illustrating the main control valve, as seen from line 8-8 on Fig. 5.

Fig. 9 is a vertical, transverse, sectional view through the drilling head takenon a plane for- 5 wardly of the plane of Fig. 8 as seen from line 9-9 on Fig. 5. c

Fig. 10 is a fragmentary, vertical, sectional view through a portion of the drilling head taken on a plane behind the plane of Fig. 8 on line l0l0 on Fig. 5.

Fig. 11 is a fragmentary, sectional view taken 'at right angles to Fig. 9 on line ilii on said Fig. 9.

Fig. 12 is a fragmentary, transverse, sectional view taken on line i2--|2 of Fig. 9.

' Fig. 13 is an enlarged, sectional view through a portion of the drilling head as seen from line l3|3 on Fig. 3.

Fig. 14 isan enlarged, fragmentary, vertical,

, vation, and partly in section, illustrating certain 5 of the central parts as seen from line l5l5 of Fig. 3.

Fig. 16 is an enlarged, fragmentary, vertical,

sectional view partly in elevation and partly in section, as seen from line l6l6 on Fig. 3. 4

Fig. 1'7 is an enlarged, fragmentary, horizontal, section view taken on linen-l1 of Fig. 3.

Fig. 18 is an enlarged, sectional view through the valve operating means as seen from line ll--l3 on Fig. 6.

Fig. 19 is an enlarged, sectional view through a valve shifting part as seen from line l6l3 on Fig. 3, and forming a detail of the invention;

and

Fig. 20 is a diagrammatical view depicting the 20 complete hydraulic circuit, utilized in eflecting and controlling the movement of the drill or other tool carrier.

Throughout the several views of the drawings similar reference characters are employed to denote the same or similar parts.

As was noted above, this invention pertains primarily to control means for effecting step drilling operations, that is, drilling operations in which the drill is alternately fed into a work piece and retracted for chip clearance, when effecting long cuts, or operating on hard material which will not permit of a continuous operation. This invention is illustrated in the drawings as applied to a single spindle, high speed, vertical drilling machine, but it is to be understood that the invention may be applied to horizontal or other types of machinetools as well as multiple spindle drilling or other types of machine tools.

Specifically referring to the drawings, the machine therein comprises a base 25, from which rises a column 26. The column 26 is provided on its forward face with a dovetail V-guide 21 received in a correspondingly shaped guideway formed'in a plate or bracket 28 of a table 29. The table 29 is adapted to support work pieces or the like to be operated on by the tool, and this table 29 is vertically adjustable relative to the column guideway 21 and it is therefore to be understood that any suitable means may be provided for effecting the vertical adjustment of the same.

Mounted on the column 26 is a second column 36 terminating at its upper end in a goose-neck 3i from which projects the spindle drive mechanism, indicated in the drawings by the reference numeral 32. The spindle drive mechanism is illustrated in section and detail in Fig. 4, to which reference is now to be had.

As seen in Fig. 4, the spindle drive mechanism comprises a housing 33 in which is secured the stator 34 of an electric motor. Within the stator 34 is the rotor' 35 secured to the central portion of a motor shaft 36. The motor shaft 36 is mounted at each end in suitable anti-friction bearings, respectively carried by a cap 31 and a lower cover plate 38. Adjacent each of the said bearings and disposed within the housing 33, the motor shaft 36 has secured to it, fans 39 and 46 for air cooling the motor during its operation. Above the anti-friction bearing, carried by the cap 31, the motor shaft 36 has keyed or otherwise Secured to it a pinion 4|. The pinion 4| is meshed with a gear 42 keyed or otherwise secured to a sleeve 43 disposed within the housing 33 u and rotatably mounted in anti friction bearings amass? respectively carried by the cap 31 and the lower cover plate 33. The pinion 4| and gear 42 are changeable gears and may be inter-changed'on their mountings or other pinions and gears substituted therefor to change the rate of rotation of the sleeve 43 as is well known in usual practice. The cap 31 is closed by means of a top cover plate 44. The sleeve 43 is provided interiorly thereof with a suitable key or keys adapted to enter a key-way or splines 45 formed in the exterior of the drill or other spindle 46 which telwcopes with the said sleeve 43. The spindle 46 projects below the drive mechanism, and is joumalled for rotation in an anti-friction bearing 41 and a quill 46 each carried by aspindle carrier 49, illustrated most clearly in Fig. 7. Below the quill 46 the spindle is provided with the usual socket 50 for the drill or other tool. In order to adjust the spindle and, therefore, the tool carried thereby, relative to the carrier 49, the quill is provided on one face thereof with rack teeth 5| meshing with a rack pinion 52 securedto which is the shaft 53 rotatably journaled in the carrier 49. Ahead of the carrier, the shaft 53 is provided with a knob 54 whereby said shaft-and its pinion are rotated. To secure the quill in adjusted position the carrier 49 is split at its lower end, as at 55, and disposed on each side of the slit is an ear 56 through which passes a clamping bolt 51. The operation of this clamping mechanism is well understood.

The carrier 49 is provided on the rear end with a dovetail guide 58 received in a corresponding guide-way 59 formed in the forward face of the drill head housing 60; see Figs. 5 and 6. Disposed within the guide-way 59 and adjacent to the carrier guide 58 is a gib 6! for taking up play and wear as soon as it develops within the guide-way. The drill head housing 60 is provided in its rear face with a dovetail guide-way 62 receiving a similarly shaped tongue 63- projecting from the forward face of the machine column 30. Disposed in the guide-way 62 and adjacent to the guidetongue 63 is a clamping gib 64 for securing the drill head in position on the column 30.

In practice, the drill head housing 60 is normally non-adjustable and immovable relative to the support column, while the carrier 49 is moved relative to the drill head to effect the movement of the tool toward the work, through the work and from the work. This carrier may be moved by any suitable or desirable means, but preferably by hydraulic means as illustrated in the drawings and as will now be described.

As seen in Fig. 7, the drill head housing 66 is provided in its lower end, immediately behind the carrier 49, with a recessed or cutout portion 65 into which projects'a lug 66 integral with and projecting rearward from the carrier 49. The lug 66 is provided with an aperture, through which projects a reduced portion 61 of a piston rod 66. The lug 66 is secured to the reduced portion by clamping same between a nut 69 and a shoulder at the other end of the reduced portion 61. Secured to the upper end of the piston rod 68 is a piston 16 adapted to be actuated through a. sleeve or cylinder ll mounted in a suitable bore in a drill head housing 69. The upper end of the cylinder II is closed by a cylinder head 12 which is secured by suitable cap screws or the like to the housing 60. The lower end of the cylinder II is closed by a-suitahle stuffing box construction 13 anchored against movement by the screw 14. The piston rod 43 passes through the stumng box 13 in its move- 15 tural views of the parts as they. are encountered while describing the circuit and parts as illustrated in the diagrammatic view. 1 Accordingly, there is shown a sump or tank I5 which may be formed within the base of the machine, or within the column 26 or may be a separate unit disposed entirely externally 1 of the machine. Above the tank I5 is a pump 16 having the intake side thereof connected by a suction pipe or conduit I! with the tank. Projecting from the other. or discharge sideof the pump 16 is the pressure pipe or conduit 18 which go terminates at its other end in the main control valve, indicated in general in Fig. 20 by the reference numeral I9. The pressure pipe or conduit I8 has connected therewith one end of a by-pass pipe or conduit 80 which terminates at its other .95 end in the sump or tank 15. The by-pass pipe or conduit 80 has therein a. pressure relief valve 8I which is set to determine the operating pressure in the circuit.

The main control valve mechanism 19 is shown so structurally in Fig. 8 and comprises a valve block 82 secured to the inner face of a plate 83 on the drill head housing 60 and interiorly of which the said valve block 02- is located. The valve block 82 is provided with a bore 84 in which is placed a valve sleeve 85. The valve sleeve 85 is provided with a plurality of sets of radial ports 86, 81, 88, 89, 90, and 96, each of which sets is encircled by a similar circumferential groove 92 disposed in the exterior of thevalve sleeve.

By referring to Fig. 20, it will be noted that it is with the radial ports 88 which the pressure pipe or conduit l8 connects. The ports 86 have connected therewith one end of a pipe or conduit 93 which is the return conduit, while the ports 9| have connected therewith one end of a supplementary return pipe or conduit 90 which terminates at its other end in the return conduit 93. The ports 81 have connected therewith one end of a pipe or conduit 95 which terminates X50 at its other end in a port at the upper end of the cylinder II, while ports 89 have connected therewith one end of a pipe or conduit 90 which terminates at a port at the lower end of said cylinder II. The remaining set of ports 90 have likewise connected therewith one end of a pipe or conduit 91 which terminates at its other end in a balance valve mechanism indicated in general in Fig. 20 by the reference numeral 98. It should be noted at this time that while the several ports of the valves and cylinder have been described as connected to one another by pipe or conduit, these connections frequently take the form of ports interdrilled in the valve block 82 and they are to be so interpreted.

Disposed within the bore in the valve sleeve 85 is a sliding piston type valve 99 having formed throughout its length a plurality of cannelures or reduced portions I00, I0! and I02 adapted,

when the valve is in different positions, to connect the ports-through the valve sleeve in differ ent combinations. The valve member has four operative positions which are; first, the stop position or that illustrated in the drawings; second, a position to the right of that shown in Fig. 20

and beneath that shown in Fig. 8 which is the return position for elevating the tool carrier or returning it to the starting position; third, a position to the left of that shown in Fig. 20 and above that shown in Fig. 8 which is the feed position or the position when the carrier is being moved downwardly at a slow feeding rate; and fourth, a position to the extreme left of that shown-in Fig. 20 and extreme vertical position above that shown in Fig. 8 which is the rapid forward position or a position wherein the carrier is being actuated downwardly at a rapid rate of speed toward the work.

The valve member 99 is moved to the various positions by manual and power means; the manual means beingutilized for initially starting a cycle of movement and the power means for effecting a cycle when it is once started. This manual means, as shown in Figs. 3, 6 and 14, comprises a lever I03 which is pinned or otherwise secured vto the outer end of a shaft I00. The shaft I04 is journalled in a bearing sleeve I05 carried by the drilling head plate 83 and projecting inwardly therefrom and pinned or otherwise .,secured to. the inner end of the shaft I04 is an'arm I06 which carries at its free end the valve shifter stud I01; see Fig. 6. The head of the valve shifter stud I0! is received in a transverse slot I 09 formed in the valve stem I09 projecting downwardly from the valve member 99 as illustrated in Figs. 6 and 8. The valve stem I09 is journalled for sliding movement in a valve block H0 located beneath the valve block 82 and mounted in position within the head housing 60 being secured to the inner face of the housing plate 83.

In order to determine the several positions of the valve member 99 the valve stem 809 within the valve block 0 is provided with four notches ii i which cooperate with a springpressed detent H2 carried by the said valve block H0. In addition, the valve block II 0 carries an abutment screw 3 which determines the ultimate or final position of the valve member in one direction which is the reverse position of the, valve or position No. 2 above described.- The other limit of movement of the valve member is determined by a second abutment screw Ild threaded through the upper end or wall of the drill head housing 00 and this position of the valve is the 8 rapid rate position or position No. 4, as above described.

With the parts in the position illustrated in the drawings, the lever I03 is actuated in a clockwise direction about the axis of the shaft as seen in Fig. 3. This will, of course, shift the valve member 99 downwardly to the limit of its movement and effect a rapid movement of the piston 10 and,'therefore, the spindle carrier 49.

The flow of the hydraulic medium, see Fig. 20,

is by'way of the main pressure pipe orconduit 18 to the port 88 of the valve mechanism 19, through the cannelure or reduced portion I0! of the valve member 99 to the ports 89 and the pipe or conduit 96. The flow continues through the pipe or conduit 96 to the lower end of the cylinder II and acts on the under-surface of the piston 10 for elevating same. The fluid ahead of the piston is forced out through the pipe or conduit to the ports 81 of valve mechanism I9 through the cannelure or reduced portion I00 to the port 86, discharge pipe or conduit 93 and sump or tank 15. This upward movement of the piston I0, and parts actuated thereby continues until the valve member 99 is shifted either automatically or manually to the position illustrated 73 movement of the handle I03 shifts the valve.

member 99 to its extreme left hand position, as

seen in Fig. 20 or its extreme uppermost position,

as seen in Fig. 8. With the valve in this position, the flow of the hydraulic medium is from the pump I5 through the pressure conduit I8 to the valve mechanism I9 where it is connected, by the v cannelure or reduced portion IOI, of the valve member 99, with the pipe or conduit 95 and the upper end of the cylinder II. The piston 10 is thereby driven downwardly forcing the medium ahead of the piston from the cylinder II through the pipe or conduit 90 to the valvemechanism I9, where the said medium is connected, by way of cannelures or reduced portion I02, of the valve member 99, with the supplementary discharge pipe or conduit 94 and pipe or conduit 93 and therefore the tank or sump I5. This movement of the piston continues until the valve member 99 is shifted.

The shifting of the valve member 99 is effected automatically by means of a dog mounted on the carrier 49. As seen in Figs. 3, l6 and 18, this rapid traverse dog II5 comprises a sleeve-like body portion H9 from one side of which projects a nose III, while from the other side pro jects a lug H8. The lug H8 is hollow and has imounted therein a friction shoe II9, backed up by a spring I whose tension may be varied by a threaded end plug I2I. The friction shoe II9 bears against one side of a rod I22 mounted at its upper end in a bracket I23 secured to the carrier 49, and at its lower end in a bracket I24 likewise carried by the carrier 49. This rod I22 will hereinafter be referred to as the cumulative dog rod. The rapid traverse dog is positioned in the first instance on the rod I22 at a point just before the drill orother tool in the socket 50 contacts the work and when this point is reached, the nose III thereof engages the adjacent face of a flipper member I25 which is keyed or otherwise secured to the outer end of a shaft I26 journalled in the drill head plate 83. As will be seen in F g. 3 the flipper member I25 is provided, at its lower end, with a notch I21 in which is disposed the ball ended lug I28 projecting from the hub of the lever I03. From this, it will be seen that any movement imparted to the flipper I25 will be transmitted to the lever I03 and any parts carried thereby, and conversely any movement given to the lever I03 will be transmitted to the flipper I25.

This movement of the flipper I25 through the parts connected with the lever I03 shifts the valve member 99 toward the right or to the third position above referred to which, as was noted above, is the feeding position and causing the tool to travel through the work at the proper feeding rate during the tooling thereof. At this time, the flow of the hydraulic medium through the valve mechanism I9 by way of the-pipe or conduit 99 is stopped and this flow is shunted through pipes or conduits I29 and I90. The former of the pipes or conduits terminates in a metering valve mechanism indicated in general in Fig. 20 by the reference character "I, while the latter of the conduits terminates in the balance valve mechanism 90. It is the metering valve mechanism I3I which determines the rate of feed of the drill or tool and this mechanism is structurally illustrated in Fig. 10, to. which reference is now to be had.

As seen in- Fig. 10, the metering valve mechanism I3I comprises a block I32 which is secured to the rear surface of the valve block 92 as seen in Fig. 5. The block I32 is provided therein with a bore I33 which communicates at one end with a chamber I34 formed in the block I32. The chamber I34 is closed by a cap plate I35 having projecting therefrom a lug I35 and having an internally threaded bore I31. The threaded bore I31 is in axial alignment with the bore I33 in the block I32 and disposed in these aligned bores is the metering valve member I 30. The valve member I38 is provided intermediate its ends with an enlarged portion I 39 threaded in the bore I31 and projecting from one side of the enlarged portion I39 is the valve portion I40, while projecting from the other side is the stem I4I utilized in adjusting the position of the valve member relative to the bore I33. The valve portion I40 has formed longitudinally thereof, a

groove I42, which increases in depth as it runs from' the enlarged portion I39 to the free end thereof. This groove I42 controls the rate of flow from the chamber I34 through the valve port I33 and therefore controls the return of flow through the whole system during the feeding of the tool. Entering the chamber I34 is a port I43 and, it is with this port that the pipe or conduit I29 connects.

The balance valve mechanism 99 is employed to control the rate of flow through the system as established by the meter valve mechanism and prevents any fluctuation of flow in the system which may be caused either by extra hard portions in the work or by soft or void portions therein. This balance valve mechanism is structurally illustrated in Fig. 10, and as there shown, utilizes the same valve block I 32 which houses the metering valve mechanism. This balance valve structure comprises a valve member I44 disposed in a second bore I45 in the block I32. The valve member I44 is of the piston type and has formed thereon a cannelure or reduced portion I46 which, through a conical shoulder I" at one end thereof, controls the flow through a. port I48. Communication is had between the metering valve bore I33 and balance valve bore I45 by means of a port I49. In addition, the

metering valve bore I33 communicates, by means of a port I50 with the balance valve bore I45 at a point ahead of the valve member I44. Disposed in the portion of the balance valve bore I45 ahead of the valve member I44 is a spring I5I which cooperates with the fluid on this side of said valve member and supplied by way of the port I50. The other or rear end of the'balance valve member I44 communicates with the chamber I34 and is therefore subjected to the pressure entering said chamber by way of the pipe or conduit I29.

It is believed that the operation of this balance valve is understood by those conversant with this art and, briefly, is as follows:

The flow into the chamber I34 is greater than the outward flow through the gioove I42 which causes a build up of pressure on the valve member I44 for shifting it to a position for restricting the flow through the port I48. At the same time, the flow through the groove I42 into the bore I33 flows through the port I58 and builds up a pressure which cooperated with the spring I5I for shifting the valve member I44 against. the pressure in the chamber I34. These forces shortly balance one another to a point for effecting the flow through the port I48 at a rate in accordance with the setting of the meter valve member I88. Should, for some reason or other, the carrier tend to coast ahead, the increased flow into the chamber I34 would shift the balance valve member I44 to further restrain the flow through the port I48 and thereby prevent the said coasting. n the other hand, should the carrier tend to slow up, the reduced flow into the chamber I34 would means reduce the pressure on the balance valve member I44 and thereby permit the spring II' to shift the balance valve member I44 to open the flow through the port I48 and bring the rate of movement of the carrier up 'to its normal rate of movement.

It should be noted at this time that the ports I49 and I58 connecting'the bores of the meter valve member I38 and balance valve member I44 with one another are shown on Fig. 20 as pipes or conduits bearing the same reference numerals. It should also be noted that the outlet port I48 from the bore I45 is the port with which the pipe or conduit 81 from the valve mechanism 18 is connected and that, in practice, the pipe 81 is a port connecting between the main valve block 82 and the valve block I32.

Continuing the description of the flow of the hydraulic medium when the carrier is being actuated at a feeding rate of speed, the flow is from the cylinder ll through the pipe or conducit 86, branch pipe or conduit I28, restricted passage or groove I42 to the ports, pipe or conduits I48 and I58 to .the balance valve mechanism 88. The

flow through this mechanism, as described above,

is determined by the setting of the meter valve member I88 to the pipe or conduit 81 and main valve mechanism 18. The medium is connected through the valve mechanism 18 with the discharge pipe or conduit 88 and discharge pipe or conduit. 88 and therefore the sump or tank 15.

The tool carrier continues to move at this relatively low feeding rate of speed until the valve member 88 is again shifted. This shifting of the valve now takes plane by power means, entirely dissociated from the carrier, but which power ontrolled or operated by the carrier. For his purpose there is mounted on the cumulative stop dog bar, a dog I5I, illustrated in Figs. 8, 15, 16 and 18 and comprises a body portion I52 through which is formed the aperture for the rod I22. Projecting from the body portion I52 is an arm I53 through which is threaded a trip or dog screw I54 having a terminal or nose portion I55. The dog screw I54 is adjustable through the arm I53 to determine the amount of feeding movement which the carrier is given, prior to reversal, and the screw is locked in position by a lock-nut I56. Opposite one face of the cumulative dog bar I22 the dog I5I is provided with a slot I51, see Fig. 16. Disposed within said slot is a ratchet pawl I58 pivoted at I58 intermediate its ends to the dog I52. The pawl I58 is provided at its lower end with a tailor lug I68 which projects beyond the body lines of the dog I5I. The upper end of the pawl I58 is provided with a nose I 8| adapted to successively engagethe ratchet teeth I62 formed in one face of the rod I22. Projecting from the pawl I58 adjacent to the nose IN is the dog I52.

pin I83 forming an anchor for one end of a coil spring I64 which has its other end anchored to a pin I65 projecting from a dog I5I. The spring I64 at all times urges the pawl I58 in a clockwise direction about the pivot I58 and thereby maintains the nose I6I in proximate engagement with the ratchet teeth I62.

As seen in Fig. 18 the'rapid traverse dog H5 is spaced beneath the feed dog I5I and these dogs are normally spaced from one another by an expansion spring I66 which abuts on its, lower end with the upper surface of the rapid traverse dog H5 and on itsupper end with the under surface of the' feed dog I52. In order to limit the space between these dogs the arm I 53 of the feed dog is provided with a bore I 81 through which extends the body portion of a stud I68. The stud I68 has its one end threaded into the rapid traverse dog H5 and has its upper end provided with a head I69 which lies on the upper surface of the feed From the foregoing it will be seen that this stud I68, being carried by the rapid traverse dog I I5 limits, through the head I68, the separation of the rapid traverse and feed dogs, as effected by the spring I66.

Shortly after'the rapid traverse dog 'II5 has changed the rate of movement of the carrier from rapid to feeding rate, depending of course upon adjustment of trip or dog screw I54, the tip or nose I55 of the dog screw engages the upperend I18 of a slide, IlI for shifting the main valve member 99 from its feeding position to its return position, which. is the position to the right of that shown in Fig. and beneath that shown in Fig. 8. This shifting of the valve is effected as follows. 6

The slide I'll is mounted in a guide-way formed by an arm I12 projecting from a bracket I13 and opposed to the forward face I14 of the drill head plate 88 as seen most clearly in Figs. 13 and 1'7. As seen in Fig. 18 the slide III is provided on its inner face with rack teeth I15 meshing with a segmental rack pinion I16 integral with or secured to hub I11 of a short arm I18. The hub I11 ismounted for oscillatory or rotation movement on the bearing bushing I85 which, as noted above, is carried by the drill head plate 83 and f projects interiorly thereof. The arm I18 of the hub I11 has its free end I18 disposed at a point inwardly of the hub I11 and has contacting same on opposite sides thereof plungers I88 and I8I. These 'plungers are, in reality, valve stems, shown structurally in Figs. 9, 11 and 12, and diagrammatically in Fig. 20 and the description will now be continued with reference to the plunger I88 which effects the present shifting of the main valve 99 and which is operated through the slide I" and trip or dog screw I54.

The plunger or valve stem I88 has integrally connected with its inner end the valve member and is mounted for movement in a bore I82 formed in the valve block 82, as seen in Fig. 9. The said valve is provided with a reduced portion or cannelure I83 and is further provided at its extreme inner end with a counterbored portion I84 in which is mounted one end of a spring I85. The spring I85 is disposed at its other end in a spring seat I88'formedin a spring abutment member I81. v The spring abutment member I81 is rigidly mounted in a bore I88 formed in the valve block 82 and in axially alignment with the valve bore I82. These bores are, however, of different diameters thereby forming a shoulder against which an enlarged portion I88, on the valve abuts to limit the movement thereof, as effected by the spring I95.

This valve mechanism just described, is diagrammatically illustrated in Fig. 20 and is referred to in general by the reference-numeral I99. As here shown, the valve member is disposed within the sleeve I9I which is mounted in a casing, such as the valve block 92, although,

in practice, this sleeve may be dispensed with.

10 Formed through the sleeve is a plurality of sets of radial ports I92, I93 and I94 each of which is encircled by a circumferential groove I95 formed in the exterior of the sleeve I95. Connecting with the ports I92 is one end of a pipe or con- I duit I96 which terminates at its other end in the connected therewith one end of a pipe or conduit I98 which terminates at its other end in a piston mechanism, indicated in general in Fig. 20

by the reference numeral I99.

This piston mechanism I99 is shown strucg turally in Fig. 9 and comprises a piston 299 disposed in a bore or cylinder 29I, formed in the valve block 92. As shown in Fig. 9, the piston 299 abuts on its free end with the upper face of the valve shifter arm I96 while, as shown diagrammatically in Fig. 20, this piston 299 abuts directly with the adjacent end of the valve member 99. It will be appreciated that movement of the piston will, either-directly or through the connection of the arm with the valve, efiect the shifting of the valve. The movement of the valve as effected by the piston 299 is to the extreme right hand position as seen in Fig. 20 or the lower-most position as seen in Fig. 18, which is of course the reverse position, and eflects therapid return of the carrier and parts carried thereby.

It is believed thatthis operation is readily understood without a detail description of its operation, when it is remembered that engagement of the trip or dog screwI54 with the slide I1I operates the arm I19, thereby connecting the pressure through the pipe, conduit, port or the like I91 with the pipe or conduit I99 and thereby shifting the piston 299. As soon as the piston 299 50 positions the valve member 99, the spring pressed plunger II2 holds the valve in this position and, upon retraction of the carrier, the dogscrew leaves the slide I1I, whereupon -the spring I95 returns the valve to the position illustrated in the drawings, thereby connecting the rear end of the piston with the sump and relieving the pressure thereon so as not to interfere with the subsequent movement of the valve which is opposite to that just described.

This upward or retracting movement of the carrier continues to a point which is substantially the point from which the initial movement took place but is in fact a short distance below the point for a reason to be later described. The means for stopping the upward or retracting movement of the carrier is as follows.

The cumulative dog rod I22 has secured to its lower end an arm 292, from which projects a pin 293. This pin 293 is adapted in its upward 7o movement to shift the slide I1I in a reverse direction from that above described and operates through a yieldable pin mechanism most clearly illustrated in Fig. 19. This pin mechanism comprises a housing 294, which is in reality the outer 7; end of an arm 295, see Figs. 3 and 13. The housment of the carrier.

mg 294 is provided therethrough with a counter bore 299, thereby providing a shoulder 291. Besting on the shoulder 291 is the enlarged collar portion 299 of a pin 299, which projects above and below the housing 294. face 299 is one end of a spring 2I9 which abuts at its other end a plug 2, which closes the counterbore 299; the spring 2" at all times urg ing the pin 299 downwardly to the position shown in Fig. 19. when the parts are in normal posttion the pin 299 is in axial alignment with 299 and these pins underlie the. lower face 2I2 of the slide I"; the pin 299 being in close proximity thereto, while the pin 299 is brought into engagement with the pin 299 upon the upward move- As soon as the carrier getsto the upper point, 'the slide III is shifted this time upwardly and causing the arm I19 to depress the plunger or valve stem III.

The valve stem I9I, similar to the valve stem' m- I99, has integrally with, or secured to its inner end, the valve and is mounted in a bore 2I9; formed in the valve block III. This valve is substantially identical with the valve stem I99 and has intermediate its ends a cannelure or re- "29 duced portion 2 and is provided in its extreme end with a counterbore 2I5. Seated in this counterbore 2I5, is one end of a spring 2" which has its other end disposed in a spring seat 2I1 formed in a spring abutment 2I9. The sprinrw abutment 2I9 is secured in a bore 2I9 whichis in axial alignment with the bore 2I2. These bores 2I9 and.2I3 are of different diameters, thereby providing a shoulder, against which an enlarged collar portion 229 on the valve, abuts'll goslimit its movement as eifected by the spring This valve mechanism is diagrammatically illustrated in Fig. 29 and indicated in general by the reference numeral HI and as there shown 18 40 substantially identical in construction with the valve mechanism I99. This valve mechanism is again illustrated as including a valve sleeve 222 pressed into a casing or valve block, which casing may be dispensed with as illustrated in Fig. 9.45 The sleeve 222 is shown as having a plurality of sets of radio ports 222, 224 and 229, all entering the valve bore 2I3 and each set of ports being encircled by a circumferential groove 229 formed in the exterior of the sleeve 222. Connected with the ports 223 is one end of a pipe or conduit 221 which has its other end connected with the pressure pipe or conduit 18. The ports 225 have connected therewith one'end of a pipe or conduit 229 which terminates at its other end in the- 5 sump or tank 15. The remaining set of ports 224 have connected therewith one end of the pipe or conduit 229 which terminates at its other end in a piston mechanism, indicated in general by the reference numeral 239 which is similar in all respects with the piston mechanism I91. This piston mechanism 239 is illustrated structurally in Fig. 9 and as there shown comprises a piston 23I mounted in a cylindrical bore or cylinder 232 formed in the valve block I I9.

The operation of this mechanism is identical with the operation of the piston mechanism I99 since either it abuts directly with the valve member as illustrated in Fig. 20 or with the valve shifter arm, as illustrated in Fig. 9. The valve member 99 is shifted to its other extreme posi-' tion, which is to the left, as seen in Fig. 20 or upwardly as seen in Fig. 8. Again, as soon as the carrier is moved and restraint taken from the slide Hi the valve is returned to its normal posi- Resting on the upper tion by the spring 2 I 5 to relieve the pressure from the piston 23I and offers no interference to the subsequent movement of the valve member.

With the valve in the position to which it has now been shifted, the carrier is again started downwardly at a rapid rate of speed and continues at this rate of speed until the rapid traverse dog II5 shifts the valve to the position above described, thereby changing the rate of movement of the carrier to a relatively slow feeding rate of speed. The point of change in the rate of movement is now below that initially since the tool is carried at the rapid rate to the point where the previous tooling operation stopped. This increase in rapid traverse distance was occasioned by allowing the rapid traverse dog to slide relative to the dog bar I22 even though the feeding dog was connected with the bar and continuing to move therethrough the rack and pawl mechanism I58-I62. The rapid traverse dog was held against movement by a face 233 on the bracket I13 upon which it rests, immediately after shifting the valve to its slow feeding rate of speed. In order to return the feed dog to its initial position after each feeding stroke the drill head has secured to it a cam plate 234 provided at its for ward end with cam faces 235 and 236, the latter of which. during the return of the carrier, engages the tail or lug I60 of the pawl I58 for actuating the same in a counterclockwise direction, thereby disengaging the pawl nose ISI from the ratchet teeth I32 and permitting the spring I66 to expand and establish the initial spacing of the rapid traverse dog and feed dog, as determined by the connecting stud I88. It will therefore be appreciated that during the feeding stroke the rapid traverse dog I I5 is held with respect to the movement of the dog rod I22 while the feed dog is moved therewith, due to the positive connection established by the ratchet and pawl mechanism .I56-I62. Upon the completion however of a feeding stroke the parts are again returned to their original positions, whereupon the carrier is actuated at a rapid rate to the point where the previous tooling operation stopped and a second tooling operation performed. As soon as the trip or dog screw I54 again actuates the slide ill for reversing the movement of the carrier, the carrier is rapidly returned to its initial position and again reversed through the pins 203-200 and slide III. This cycle of rapid movement to the point where where the previous drilling i or tooling operation stopped, followed by a tooling or drilling operation and a rapid return is continued until the piece is completely finished. This is determined by a dog 23?, adjustably secured to the carrier 49. This dog may be referred to as the stop dog since it stops the operation of the machine until again manually started, as above described. The stop dog 23'! positions the parts, which eventually shifts the valve member 99 to the position shown in the drawings, through the means new to be described.

The stop dog 231 is adjustably mounted in a slot 238 formed vertically of the carrier 41 and is positioned to go into operation as soon as the drill or tool has completed its work. This dog 23! is formed to provide a cam face 239, which engages with the projecting end of a short rack 240, slidably mounted in a suitable bearing, provided in the bracket I13. The rack 240 has its teeth 24I meshing with a rack pinion 242 keyed or otherwise secured to an oscillatable bar 243, as shown most clearly in Fig. 17. The bar- 243 is laterally spaced from the cumulative stop rod I22 and the said bar has its opposite ends journalled by oscillatory movement in the bracket I13 and a second bracket 244, secured to the drill head plate 83. The oscillatory rod 243 has two operative positions; first, as shown in the drawings, and second, a position oscillatably spaced in a clockwise direction from that shown. In order to determine these positions, the said rod has secured to it, beneath the bracket I13, a positioning member 245 which is provided in its one end with positioning notches 246 co-operating with a spring pressed detent 247, mounted in a suitable bore in the bracket I13.

Beneath the positioning member 245 the rod 243 has secured to it the arm 205, which carries II at its outer end the pin 209, and the oscillation of which rod 243 positions the arm 205 and, therefore, its pin 209 into and out of alignment with the pin 203 on the cumulative stop rod I22. The rod 243 has further adjustably secured to it, intermediate its ends, a dog-248 having a projecting nose portion 249 adapted, when in the posi-- tion shown in the drawings, to overlie a lug 250, projecting from the adjacent edge of the rapid traverse dog II 5.

The operation and purpose of this mechanism is as follows. When the work piece has been completely tooled, the stop dog 231, through its cam face 239 engages the end of the rack 240 for shifting it to the position shown which is a .downward movement as seen in Fig. 7 or a movement to the right as seen in Fig. 2. This movement of the rack 240 efiects an oscillation of the bar 243 in a counterclockwise direction, thereby positioning the pin arm 205 as shown in Fig. 13 and positioning the dog 248 as shown in Fig. 15. The arm 205 removes its pin 209 from the path of movement of the pin 203, thereby preventing the operation of the slide Ill and the operation of the main valve member 09, as above described. 40 This then would ordinarily permit the carrier 48 to move upwardly to a position beyond that at which the previous reversal took place and such a movement is permitted, but only for a very short distance. :5

The return movement of the carrier 38 is now interrupted by a pin 25!, which projects inwardly of the carrier from a face 252, provided on the carrier and spaced a shortdistance from the face of the drill head housing, as seen most clearly in Figs. 17 and 18. This pin 25I is adapted to engage a lug 253 projecting from-the free end of an arm 254, keyed or otherwise secured to the inner end of the shaft, the outer, end of which carries the flipper I25. This movement of the arm 254 is in a clockwise direction, as seen in Figs. 3 and 18 which is of course the same movement imparted to the flipper I25 and through its slot and tongue arrangement I2I-I28 causes the counterclockwise movement of the arm I03 for positioning the main valve member, as shown in the drawings, and stopping the movement of the carrier 48.

The positioning of the dog 248 on the bar 243, as shown in'Fig. 15, causes, during this return movement of the carrier 48 through the overlapping of the dog nose 249 and lug 250, the holding of the rapid traverse dog II 5 during the movement of the carrier and this holding of the rapid traverse dog through the stud connection of the feed dog also holds it. This arrangement results in the repositioning of the rapid traverse dog and feed or cumulative feed stop dog, relative to the carrier after the completion of each work piece.

The shifting ofthe'main valve member I! to the stop position shown, po itions the starting lover I" as shown in Fig. 3, that is, in a plane and positioning the arm 2 to have its pin 20! in position to be actuated by the cumulative stop rod pin'fll; whereupon the cycle of movement again continues until the work piece now being operated upon is completed, as above described.

-It is believed that the operation of' this mechanism is understood from the foregoing'description and that a further description of the operation is unnecessary.

From the foregoing, it will now be appreciated that there has been provided a cumulative stop mechanism for effecting step drilling in which the parts are at all times positively connected c .a rapid movement dog frictionally engaging said with one another without dependance upon purely. frictional engagement of the parts to accomplish the same. It will further be noted that there has been provided a mechanism in whichea'ch step of the tooling operation is adjustable instead of having the same time duration for each workpiece as would be the result, if a fixed cam bar or the like were utilized. It should also be noted that, with the mechanism here employed, the change in rate. and direction of movement of the carrier takes place instantly without any danger of over-run and that the machine can, therefore, be very accurately set up and adjusted. mechanism or means for accomplishing the above results are relatively simple in their construction and operation, and that involved mechanisms or devices have been dispensed with.

What is claimed is: 1. In a drilling machine of the class described.

the combination of a tool carrier, power means ceding cycle, comprising a dog bar on the caring said bar for etermining the amount of rapid movement to imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movement thererier, a rapid royement dog frictionally engagof at the end of each feed movement, and means for mechanically connecting the slow movement dog to the dog bar to cause same to move' therewith after the rapid dog has been stopped.

2. In a drilling machine of the class described, the combination of a tool carrier, power means for shifting said carrier at successive rapid and feeding rates in one direction, and at arapid rate in the other direction, and cumulative stop means for determining the amount of rapid and feed movement to be imparted to the carrier for each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal to the time of the feed movement of this It' will also be noted that the preceding cycle, comprising a dog bar on the carrier, a rapid movement dog i'rictionaily engaging said bar for determining the amount of rapid movement tobe imparted to the carrier, a second dog onsaid bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movement thereof at the end of each 'ieed, movement, and means for mechanically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, said slow movementdog including an adjustable trip member, whereby the duration of the slow movement after the, rapid movement may be varied.

3. In a drilling machine of the class described, the combination of a tool carrier, power means for shifting said carrier at successive rapid and means for determining the amount of rapid and' feed movement to be imparted to the carrier for each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal ,to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier,

bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movement thereof at the end of each feed movement, means for mechanically'connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, yieldable means for normally spacing the rapid dog from the slow dog which is compressed during the slow movement of the carrier, and means for disconnecting the mechanical coupling between the slow dog and dog bar at the end of the slow movement of the carrier..

4; In a drilling machine of the class described,

the combination of a tool carrier, power means for shifting said carrier at successive rapid and feeding rates in one direction, and at a rapid rate in the other direction, and cumulative stop means for determining the amount of rapid and feed movement to be imparted to the carrier for each cycle, and for increa ing the length of duration of each succeeding cycle by an amountequal to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier, a rapid movement dog frictionally engaging said-bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction-0f movement thereof at the end of each feed movement, means for mechanically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, yieldable means for normally spacing the rapid dog from the slow dog which is compressed during the slow movement of the carrier, and means for disconnecting the mechanical coupling between the slow dog and dog bar at the end of the slow movement of the carrier, and means for limiting the separation of the rapid and slow dogs as effected by the yielding means.

5. In a drilling machine of the class described, the combination of a tool carrier,power means for shifting said carrier at successive rapid and feeding rates in one direction, and at a rapid rate in the other direction, and cumulative stop means for determining the amount of rapid and feed movement to be imparted to the carrier for each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier, a rapid movement dog frictionally engaging said bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movement thereof at the end of each feed movement, and means for mechanically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, comprising a ratchet pawl carried by the slow dog and engaging rack teeth on the dog bar.

6. In a drilling machine of the class described, the combination of a tool carrier, power means for shifting said carrier at successive rapid and feeding rates in one direction, and at a rapid rate in the other direction, and cumulative stop means for determining the amount of rapid and feed movement to be imparted to the carrier for each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier, a.

rapid movement dog frictionally engaging said bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movement thereof at the end of each feed movement, means for mechan ically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, means operable by the slow dog for eflecting the reverse movement of the carrier.

7. In a drilling machine of the class described, the combination of a tool carrier, power means for shifting said carrier at successive rapid and feeding rates in one direction, and at a rapid rate in the other direction, and cumulative stop means for determining the amount of rapid and feed movement to be imparted to the carrier for I each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier, a rapid movement dog frictionally engaging said bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movement thereof at the end of each feed movement, means for mechanically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, means operable by the slow dog for eilecting the reverse movement of the carrier, means operable after a predetermined number of cyclic movements have been imparted to the carrier for rendering the reversing means, inoperative, and supplemental means operable for stopping the movement of the carrier.

8. In a drilling machine of the class described, the combination of a tool carrier, power means for shifting said carrier at successive rapid and feeding rates in one direction, and at a rapid rate in the other direction, and cumulative stop means for determining the amount of rapid and feed movement to be imparted to the carrier for each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier, a rapid movement dog frictionally engaging said bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversing the direction of movementthereof at the end of each feed movement, means for mechanically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, means operable by the slow dog for effecting the reverse movement of the carrier, means operable after a predetermined number of cyclic movements have been imparted to the carrier by rendering the reversing means inoperative, supplemental means operable for stopping the movement of the carrier, and means for returning .the rapid and slow dogs to their normal positions, on the dog bar and relative to the'carrier, prior to the stopping of the carrier.

9. In a drilling machine of the class described, the combination of a tool carrier, power means for shifting said carrier at successive rapid and feeding rates in one direction, and at a rapid rate in the other direction, and cumulative stop means for'determining the amount of rapid and feed movement to be imparted to the carrier for each cycle, and for increasing the length of duration of each succeeding cycle by an amount equal to the time of the feed movement of this preceding cycle, comprising a dog bar on the carrier, a rapid movement dog frictionally engaging said bar for determining the amount of rapid movement to be imparted to the carrier, a second dog on said bar for determining the amount of slow movement to be given said carrier, and for reversingthe direction of movement thereof at the end of each feed movement, means'for mechanically connecting the slow movement dog to the dog bar to cause same to move therewith after the rapid dog has been stopped, means operable by the slow dog for efiecting the reverse movement, of the carrier, means operable after a predetermined number of cyclic movements have been imparted to the carrier by rendering the reversing means inoper-- i ative, supplemental means operable for stopping the movement of the carrier, means for returning the rapid and slow dogs to their normal positions, on the dog bar and relative to the carrier, prior to the stopping of the carrier, and manually operated means for initiating a cycle of movement of the carrier.

10. In a drilling machine of the class described, the combination of a tool carrier, a hydraulic mechanism including a piston for actuating the carrier through a predetermined number of cyclic movements, each cycle of movement of the carrier being at a rapid and a slow rate in one direction followed by a rapid rate in the opposite direction, control means for said hydraulic means including a valve. member having a plurality of operable positions, manual means for shifting said valve to a position for initiating a cycle of movement of the carrier, a slip dog means operable for changing the rate of movement of the carrier, and cumulative stop means for reversing the direction of movement of the carrier including a positive mechanical couple between the same and the carrier whereby succeeding cycles of movement of the carrier is progressively increased.

11. In a machine tool organization of the class described, the combination of a tool carrier, a piston connected with said carrier to efiect its movement, a hydraulic circuit for actuatingthe piston, including a main valve having a plurality of operative positions, manual means for shitting the valve to its initial starting position to efiect a rapid movement of the piston and carrier, a first power means for shifting the valve to change the rate of movement of the piston and carrier from a rapid to a slow rate, a second power means forreversely shifting the valve to its initial position to reverse the direction of movement of the-piston and carrier, independent valve mechanism for each of said two last mentioned power means,

and dog means carried by said carrier for actuating the valve mechanisms for said power means.

.12. In a machine tool organization of the class described, the combination of a tool carrier, a piston connected with said carrier to eiiect its movement, a hydraulic circuit for actuating the piston, including a main valve having a plurality of operative positions, manual means for shifting the valve to its initial starting position to effect a rapid movement of the piston and carrier, a first power means for shifting the valve to change the rate of movement of the piston and carrier from a rapid to a slow rate, a second power means for reversely shifting the valve to its initial position to reverse the direction of movement of the piston and carrier, independent valve mechanism for each of said two last mentioned power means, and dog means carried by said carrier for actuating the valve mechanisms .for said power means, and additional stop means on said carrier for shifting said main valve to a stop position described, the combination of a tool carrier, a,

piston connected with said carrier to efiect its movement, a hydraulic circuit for actuating the piston, including a main valve having a plurality of operative positions, manual means for shifting the valve to its initial starting position to effect a rapid movement of the piston and carrier, a first power means for shifting the valve to change the rate of movement of the piston andcarrier from a rapid to a slow rate, a second power means for reversely shifting the valve to its initial position to reverse the direction of movement of the piston and carrier, independent valve mechanism for each of said two last mentioned power means, and dog means carried by said carrier for actuating the valve mechanisms for said power means. and additional stop means on said carrier for shifting said main valve to a stop position for stopping the movement of the piston and carrier, the dog means for one of said power shifting means valves being cumulative, whereby its point of operation progressively advances.

14. In a machine tool organization of the class described, the combination oi a tool carrier, a piston connected with said carrier to eflect its movement, a hydraulic circuit for actuating the piston, including a main valve having a plurality of operative positions, manual means for shifting the valve to its initial starting position to efiect a rapid movement of the piston and carrier, a first power means for shifting the valve to change the rate of movement of the piston and carrier from a rapid to a slow rate, a second power means for reversely shifting the valve to its initial position to reverse the direction of movement of the piston and carrier, independent valve mechanism for each of said two last mentioned power means, dog means carried by said carrier for actuating the valve mechanisms for said power means, additional stop means on said carrier for shifting said main valve to a stop position for stopping the movement of the piston and carrier,

the dog means for one oi said power shifting means valves being cumulative, whereby its point of operation progressively advances, and means in said circuit for varying the fiow therein to vary the slow rate of movement of the carrier.

. 15. In a step drilling machine of the class described, the combination of a tool carrier, a piston .operatively connected with said carrier, a hydraulic circuit for actuating the piston and the carrier including a four position valve, a

manually operated lever connected with the valve for shifting same to a starting position for actuating the piston and carrier at a rapid rate in a 'given direction, dog means on the carrier for shifting the valve to its initial position for again actuating the piston and carrier at a rapid rate in a given direction, said first mentioned dog means'being cumulative and being advanced during each cycle of movement of the carrier an amount equal to the slow movement imparted thereto, stop means operable after a predetermined number of cyclic movements for rendering the second dog controlled power valve shifting means inoperative, means associated with said carrier shifting the valve to a stop position for stopping the movement of the piston and carrier after the second dog controlled power means has been rendered inoperative, and means for resetting the cumulative stop means after each cycle of movement of the carrier.

16. In a step drilling machine of the class described, the combination of a tool carrier, hydraulic means for actuating the carrier through repeated'cycles in advancing and retracting directions, each cycle including a rapid movement, followed by a slow movement in a feeding direction, and a rapid movement in a retracting direction, a multi-position control valve in the hydraulic circuit, a valve shifting lever connected with the control valve, manual means connected with the lever for shifting the control valve to a starting position and initiating the rapid movement of the carrier in a feeding direction, dog

means on the carrier for actuating the lever for shifting the control valve to change the rate of movement of the carrier, a hydraulically actuated piston acting on the lever for shifting the same and the valve to reverse the direction of movement of the'carrier, a. valve for connecting the piston with the hydraulic circuit, dog means on the carrier for actuating the piston control valve, and additional means for shifting the control valve to its initial position for again effecting a rapid movement of the carrier in a feeding direction. a

17. In a step drilling machine of the class described, the combination of a tool carrier, bydraulic means for actuating the carrier through repeated cycles in advancing and retracting directions, each cycle including a rapid movement, followed by a slow movement in a feeding direction, and a rapid movement in a retracting direc- 7i tion, a multi-position control valve in the hydraulic circuit, a valve shifting lever connected with the control valve, manual means connected with the lever for shifting the control valve to a starting position and initiating the rapid movement of the carrier in a feeding direction, dog means on the carrier for actuating the lever for shifting the control valve to change the rate of movement of the carrier, a hydraulically actuated piston acting on the lever for shifting the same and the valve to reverse the direction of movement of the carrier, a valve for connecting the piston with the hydraulic circuit, dog means on the carrier for actuating the piston control valve, and additional means for shifting the control valve to its initial position for again effecting a rapid movement of the carrier in a feeding direction, the first mentioned dog means being cumulative and advancing the carrier at a rapid rate in a feeding direction to the point of previous reversal.

18. In a step drilling machine of the class described, the combination of a tool carrier, a piston and cylinder mechanism connected with the carrier for effecting a cyclic movement thereof,

and hydraulic means for actuating the piston and cylinder mechanism, including a multi-position valve, manually operable means for shifting the valve to initiate movement of the carrier at a rapid rate in a feeding direction, a cumulative dog for shifting the valve to change the rate of movement of the carrier to a slow feed rate in said feeding direction, a dog for shifting the valve at the end of the slow feeding movement for reversing the direction of movement of the carrier, 2. rod for supporting said cumulative stop and feed stop dogs, yielding means for separating said dogs from one another on said rod, means for limiting the separation of said dogs and maintaining them in spaced relation to determine the duration of slow feed movement, means for locking the slow feed dog to the rod during the slow feed movement, and means for releasing the slow feed dog from the dog rod. 

